Hydraulic gear



et l @L GvSheets-She ATTORNEY. I

HYDRAULIC GEAR May 6, 1930. s. v E. TAYLOR Filed March 15, 192e C? mvv. Nv@

May 6, 1930. s. v. E. TAYLORv HYDRAULIC GEAR May 6, 1930. s. v` E. TAYLOR HYDRAULIC GEAR Filed March '15, 1926 6 Sheets-Sheet I5A RSN I W .En

1 TTORNEY.

ATTORNEY.

Y esheets-'shen 4 HYDRAULIC GEAR s. v. 'rAYLoR Filed March 15, 192e 452W# mfdy/dzm 'ENTUR May 6, 1930.

May 6, 1930.

s'. v. E. TAYLOR HYDRAULIC GEAR Filed March 15. 1926 6 Sheets-Sheet 5 @www m; u w

May 6, 1930. s. v. E. TAYLOR HYDRAULIC GEAR Filed March 15, 192e 6 Sheets-Sheet 5 JNVENT@ ATToRNEx/.

Patented-May 6, 1930 PATENT OFFICE SCOTT E.` TAYLOR, F ANACONDA, MONTANA HYDRAULIC GEAR Application led March 15, 1926.( Serial No. 94,956.

This invention relates to a hydraulic gear and has for its object to provide a gear of such class, in a manner as hereinafter set forth, whereby an infinite variation of speed,

in either forward or reverse rotation, of a driven element can be obtained, with the driving means therefor rota-ting at a constant high speed in one direction and with the torque transmitted to the driven element increasing as its speed decreases.

If a cylindrical vessel is partly filled with liquid and made to rotate, the contained liquid acquires the angular velocity of the vessel and it exerts a hydrostatic pressure against the walls of the vessel whose magnitude is equal to the square of the velocity of the liquid at the point in question divided by the product of 2g times the specific gravity of the liquid.

Accordingly if there is placed a spiral shaped pipe into the liquid, there will be a total head on the liquid flowing into the pipe, due not only to the hydrostatic pressure, but also a head due to the velocity of the liquid relative to the pipe, or theztotal heazd at its o entrance will be equal tp g- -i-v-z-Z-l fv==average absolute velocity of the liquid over the cross sectional area of the pipe vof-average absolute velocity of the pipe about the center of rotation.

Also if there is placed a vane in the rapidly moving liquid, the liquid will exert a force on the vane equal to the hydrostatic pressure of the iuid against it, normal to the axis taken from the vane plus the product ofthe mass of liquid that iows over the vane in one second of time and the diiference in velocities at enwhere trance and exit of liquid relative to the same axis and 1- -cos a) where ais the total angle through which the liquid rotates before leaving the vane. If cos a, is made equal to zero,

the total force of the liquid against the vane i5 will evidently be a maximum for any given combination of speeds of the liquid and vane,

which is exactly the condition existing'in the hydraulic gear in accordance with this invention.

Further objects of the invention are to provide, in a manner as hereinafter set forth, a gear of the class referred to, which is comparatively simple in its construction and arrangement, strong, durable, compact, thoroughly efficient in its use, having a simple and positive control, readily assembled and installed with respect to a driving means thereof, and comparatively inexpensive to manufacture.

With the foregoing and other objects in View the invention consists of the novel construction, combination and arrangement of parts as hereinafter more specifically described, and illustrated in the accompanying drawings, wherein is shown an embodiment of the invention, but it is to be understood that changes, variations and modifications can be resorted to, which fall within the scope of the claims hereunto appended.

In the drawings wherein like reference characters denote corresponding parts throughout the several views i Figures 1, 1A and 1B, when taken together illustrate a longitudinal sectional view of a hydraulic gear in accordance with this invention. i

4 Figure 2 is a section on line 2-2 Figure 1A. Figure 3 is a section on line 3--3 Figure 1A. Figure 4 is a section on line 4-4 Figure 1A. Figure 5 is a section on line 5-5 Figure 1A.

Figure 6 is a section on line 6-6 Figure 1A. J

Figure 7 is a section on line 7-7 Figure 1A.

Figure 8 is a section on the line 8-8 Figure 1A.V

Figure 9 is a section online 9-9 Figure 1A.

Figure 10 is a section on line 10-10 Figure 1A.

Figure 11 is a section on line 11-11 Figure 1A.

Figure 12 is a section on line 12-'12 Figure 1A.

Figure 13 is a section on line 13-13 Figi ure 1B.

Figures 14 and 15 are fragmentary views of the valve casing'in bottom and top plan respectively.

A hydraulic gear, in accordance with this invention, comprises a driven section which is always connected to the driven shaft, a driving section which is operated from a motor, steam turbine, or other prime mover, and an intermediate or controller section.

Referring to the drawings in detail 16 indicates a housing forming a chamber 17. One end of the housing 16 is closed by an annular head plate 18 and its other end by an annular head plate 19. The plates 18 and 19 are secured to the ends of the housing in any suitable manner. The plate 18 is of greater thickness than the plateA 19 and is formed of three different inner diameters, the portion of largest diameter is indicated at 20, the portion of smallest diameter at 21 and the portign of intermediate diameter at 22. The inner diameter of the plate 19 is the same as the largest inner diameter of the plate 18. The plates 18 and 19 form the end walls for the chamber 17 The h ousing 16 is formed at its top with an opening having a tapered wall and with the wall thereof threaded. `The opening is .indicated at 23 and closed by a peripherally threaded tapered plug 24. The providing of the intermediate portion 22 at the inner edge of the plate 18 forms a shoulder 25. The plate 18 is furthermore provided with an opening 26, in which is secured a removable closure plug 27 therefor. The cylindrical wall of the chamber 17 is provided with a pair of spaced annular shoulders 28, 29. Positioned against the shoulders 25, 28 and 29 are res ectively bearing rings 30, 31 and 32. rranged against the inner side of the plate 19 or in other words against the inner edge of the plate 19 is a tbearing ring 33. Arranged within the bearing rings 30, 31, 32 and 33-are respectively bearing rings 34, 35, 36 and 37. Interposed between the associated bearing rings of each pair is a series ofv bearing balls 38. The opposed faces of the bearing rings of each pair are grooved as at 39 to provide a raceway for the balls. The bearing rings 30, 31, 32 and 33 do not revolve as they remain stationary with the housing 16 and the end or head plates 18, 19 therefor. The bearing rings 34, 35, 36 and 37 are a part of the driving section and are carried therewith during .the operation thereof. The base of the housing 16 is indicated at 40 and is formed with extensions 41 which project beyond the plates 18 and 19 and are provided with openings 42 for the passage of hold-fast devices to flxedly secure the housing in a stationary position.

The driving section includes a prime mover vwhich by way of example is shown as an electric motor 43 having its shaft 44 of the quill type and said shaft 44 extends through the plate `19 and into the chamber 17. That end of the shaft 44 within the chamber 17 is provided with an outwardly extending annular flange 45 and said shaft is furthermore formed with a peripheral shoulder 46 against which abuts the bearing ring 37 and the latter is carried with the shaft 44. Ar-

ranged within the chamber 17 and extending into the.plate 18 is a flanged collar 47 having its flange 48 of the same diameter as the flange 45 and opposing the inner face, as well as being spaced from the plate 18. The collar 47 is formed with a peripheral shoulder 49 against which abuts bearing ring 34 and the latter is bodily carried with the collar 47. The flange 45 is spaced from the inner face of the plate 19. Fixedly secured to the flanges 45, and 48 is a driving member 450 which consists of a hollow cylinder of a length to have its edges flush with .the outer faces of the flanges 45 and 48. The inner face of. the cylinder which forms part of the driving member 50 is provided throughout with longitudinally extending, spaced, radially disposed vanes 51 having tapered free terminal portions 52. Each end of each of the vanes is formed with a reduce(1 terminal portion 53 to provide a clearance for a purpose to be presently referred to.

The driving member 50 is keyed to thc flange 45 as at 54. The flange 48 is formt-.d with an opening 55, closed by a removable plug 56. The driving member 50 is supported by the bearing rings 35, 36, in connection with the bearing rings 31 and 32 and with the balls 38 interposed between such rings in the manner as shown. The inner end of the quill shaft 44 is formed with an annular groove 57 of T-shaped contour in cross section and the inner end of the collar 47 is formed with an annular groove 58 of T-shaped cross section. The grooves 57 and 58 are of the same diameter. The function of such grooves will be .presently referred to.

The controller section which is interposed between the driving section and driven section includes a pair of' quill shafts 59, 60 arranged in lengthwise opposed relation with respect to each other and further spaced an appropriate distance apart. The shaft 59 is of materially greater length than the shaft 60. The shaft 59 extends through the motor 1 43 and also through the shaft 44 and said shaft 59 projects a substantial distance inwardly from the inner end of the shaft 44. That is to say the shaft 59 extends a substantial distance from the flanged end of the shaft 44. The shaft 59 is slightly cleared4 by the shaft 44. spaced from the outer end of the motor 43 is a stationary bearing standard 61 through which extends the shaft 59 and the latter projects a substantial distance from the outer side of the standard 61. The outer side of the standard 61, at the top thereof, is formed with a bevelled clutching face 62. Connected to and slidably mounted on the outer end of the shaft'59 is a clutching member 63, having a bevelled end 64, which coacts with the bevelled face 62 of the standard 6l. The clutching member 63 is provided with an annular groove 64 and opening into said groove 64 is an opening 65 formed in said member 63. The function of theclutching member 63, aswell as the bevelled face 62 will be presenti referred to. The clutching member 63` projects outwardly a substantial distance from the 4outer end of the shaft 59. The shaft projects a substantial distance outwardly with respect to the plate 18 andv has slidably connected to its outer end as well as projecting therefrom, a clutching member 66 formed with an annular groove 67 opening into an openin 68, formed in the member 66. The outer face of the plate 18 is formed with a bevelled clutching face 69 which associates with the bevelled end 70 of the clutching member 66. f The outer end of the clutching member 63 is formed with a bevelled face 71 and the outer end of the clutching member 66 is provided with a bevelled clutching face 72. The function of the clutching member 66 will be presently referred to.

Arranged between the shafts 59 and 60, as well as being connected therewith, isa tubular member 7 3, of the cross sectional form as shown in Figure 3. The member 73 constitutes a fluid 'guiding or controlling element when held stationary, in a manner as hereinafter referred to, and a propelled element when clutched to a driven element to be hereinafter referred to. The member 73 has its periphery provided with tangentially disposed grooves 74', four in number and equally spaced with respect to 'each other and each of the same length. Each groove gradually decreases in depth from its rear towards its forward end and the forward end thereof the ports 75 and 76 are spaced from each other but communication is established between said inner ends in a manner to be presently referred to. The member 73 at each end is formed with a set of spaced stems 77 which are shrunk upon the shafts 59 and 60 and mounted upon the said shafts, as well as enclosing each set lof stems 77, is a series of segmental shaped holders 78 and one of which is provided with an opening 79,V in which is mounted a block 80. Each s'et of holders 78 has shrunk thereon a retaining ring 82, pro vided with an opening 82 in which is arranged a block 83. The block 80 is keyed to the ring 82 as at 84.

Each end of the member 73 is formed with an annular groove 85 which is T-shaped in cross section and one of said grooves oppose the groove 57 and the other the groove 58 and mounted in the opposed grooves is an H- shaped cross sectional packing 86 in the form of an annuius and constructed of -resilient -are provided by the holders 78. The end terminal portions 53 of the Yanes 51 provide clearances for the retaining rings The vanes 5l clear the high part of the periphery of the member 73. j

The driven section includes a driven shaft formed of two spaced'sections 92, 93. The

section 92 is provided with a bore 94 'whichi extends from a point removed from the outer end thereof and terminates at its inner end.

The outer end of .the section 92 carries a bearing ring 95-upon which is mounted a cage 96 carrying bearing balls 97 and surrounding the cage is a bearing ring 98. The bearing rings 95 and 98 are supported in a stationary standard 99 into which extends the outer end terminal portion of the shaft section 92. Carried by the shaft section 92 and opposing the clutching member 63 is a clutching elementl 100 having a bevelled inner face 101 whichv cooperates vwith the bevelled end 7l of the clutching .member 63. A portion of the clutching member 63 surrounds the shaft section 92 and the latter is formed with a diametrically disposed opening 102 through which extends a shifting bar 103, having its lower end mounted in an annular groove-64 and its upper end positioned in an opening 65. The groove 64 and opening 65 areformed in the clutching member 63. The actuating means for the shifting bar 103 will be hereinafter referred to. The bar 103 when actuated in one direction will move the clutching member 63 into engagement with the clutching element 100 and when moved in the other direction will shift the clutching member 63 in engagement with the bevelled face 62 of the standard 61. The shaft section 92 extends through the shaft 59 and projects from the inner end ofthe-latter an appropriate distance.

The shaft/section 93 is provided with a bore of two different diameters and that portion of the bore of larger diameter is indicated at 104 and the portion of smaller diameter at 105. Theshaft section 93 is also formed with a diametrically extending opening 106. The larger portion vof the bore 104 extends from the inner cnd of the shaft section 93 and terminates in the opening 106. The smaller portion of the bore 105 extends from the opening 106 and terminates at a point removed from the outer end of the shaft sec.- tion 93 and opens into a diametrically eX- tending opening 107. The shaft section 93 extends an appropriate distance inwardly with respect to the inner end of the'shaft 60 and further extends outwardly from the outer end of said shaft 60. The clutching member 66 carried by the shaft 60 extends around the opening 106 and projecting through the latter is a shifting bar 108 which is mounted in annular groove 67 and extends into the opcning 68 of the clutching member 66. Carried by the shaft section 93 outwardly with respect to the clutching member 66, as well as associated therewith, is a clutching element 109 having a bevelled inner end 110 which cooperates with the bevelled outer end 72 of the clutching member 66.

Mounted on the shaft section 93 is a bearing ring 111 for supporting a cage 112 provided with bearing balls 113 and surrounding the cage 112 is a bearing ring 114. The bearing rings 111 and 114 are supported by an apertured standard 115 through which extends the shaft section 93.

Extending through the opening 107 is a shifting bar 116 which is carried by a grooved collar 117 slidably mounted on the shaft section 93 and operated through the medium of a link and lever mechanism 118.

interposed between the shafts 59 and 60 and surrounding the inner ends of the shaft sections 92 and 93, as well as being secured to the said shaft sections is a fluid controller in the form of a tubular shell or casing 119, which provides a piston chamber 120. The periphery of the shell 119 is formed with a Series of lengthwise extending concavities 121 and as shown in Figure 3 each of the concavities establishes communication between the ports 75 and 76. The periphery of the shell 119 is furthermore provided with a series of concavities 122 disposed lengthwise thereof and each of which is of a greater width than either of the concavities 121. The concavities 122 are alternately disposed with respect to the Avfconcavities 121.. The concavities 122 are equally spaced with respect to each other and like arrangement is had with respect to the concavities 121.

Shiftably mounted in the bore 94 of the shaft section 92 is a piston rod 123, which extends from the opening 102 and projects inwardly from the inner end of the shaft section 92. The outer end of the piston rod 123 is secured to the shifting bar 103, as at 124. The inner terminal portion of the piston rod 123 is formed with a longitudinally extendin socket 125 which opens at the inner end o said rod 123. The piston rod 123 is formed with a series of spaced radially disposed ports 126, 127 and 128 positioned as disclosed in Figures 5, 6 and 7 respectively. The port 126 is larger than the port 127 and the port 128 is larger than the port 127. The piston rod in that portion which projects from the inner end of the shaft section 92 and in proximity to the latter is formed with a pair of oppositely extending radially dlsposed ports 129 and 130, more clearly shown in Figure 8. Carried by the inner end of the piston rod 123 adjacent to the ports 129 and 130 is a piston referred to generally by the reference character 131.

The inner terminal portion of the piston rod' 123 is of enlarged outer diameter, has its terminus outwardly flanged, see Figure 1A, and to said portion of enlarged diameter is secured a piston referred to generally by the reference character 131. y

Slidably. mounted in the enlarged portion 104 of the bore of the shaft section 93 is a tubular piston rod 132 which projectsa substantial distance inwardly from the inner end of the shaft section 93 and has its outer end terminate in the opening 106 in said shaft section 93. The outer end of the piston rod 132 is secured as at 133, to the shifting bar 108. The inner end of the piston rod 132 is enlarged and anged and has secured therewith a piston referred to generally by the reference character 131. The piston rod 132 is provided in proximity to the piston 131 carried thereby with a pair of oppositely extendin ports in the same manner as the piston ro 123 and the same reference characters 129 and 130 are employed for the ports in the piston rod 132 and such ports are arranged as illustrated in Figure 8. The piston rod 132 is also provided intermediate its ends with a port arranged in the same manner as the port 127 in the piston rod 123 and the same reference character is applied thereto. The piston rod 132 is furthermore provided with a pair of oppositely extending ports 135 and 136 shown in Figures 11 and 12 respectively and said ports are arranged in the piston rod 132 at the points indicated b the crAoss sectional lines 11'-11, 12-12, Figure 1 As the construction of each of the pistons is the same, but ,one.will be described, as the description of one will apply to the other. Each of the pistons consists of a circular disc 137 mounted on its respective piston rod and which carries a packin ring 138 having its body portion of less wi th than the thickness ofthe disc 137. Opposing the disc 137 and mounted on the piston rod is a pair of oppositely disposed cup-shaped members 139, 140 which abut the ring 138, seat on the edge of the disc 137 and are spaced from both faces of the latter. Common to and seated in a piston rod, a disc 137 and a member 140 is a packing ring 141. The elements 137 to 141 inclusive are clamped in position, by a nut 142 which has threaded engagement with the periphery of the piston rod and said nut 142, in connection with the flange 143, which abuts the member 140, fixedly secures the piston in position.

Slidably mounted in the opposed inner ends of the piston rods 123 and 132 is an elongated tubular valve casing 144 which encloses a valvular member 145 formed with length- Wise extending, spaced, semi-circular grooves 146, 147 and 148 and which constitute channels. The free end terminal 149'of the valvular member 145 is not groovechbut is of a diameter to snugly fit the inner `face, at one end, of the casing 144 whereby one end of each of the said channels is closed. The channel 146 carries the pressure liquid. The valvular member 145 forms a continuation of a valve stem 150, which is circular in cross section and closes the other ends of the channels. The valve stem 150 projects outwardly from the piston rod 132 and is mounted in the smaller portion -105 of ,the bore of the shaft section 93 and extends into the opening 107 formed in said shaft section 93 and is ixedly secured as at 150 to the shifting bar 116.

The valve casing best shown in Figures 14 and 15 has its top provided with a series of openings or ports 150, 151, 152, 153 and 154 and which are arranged in spaced relation. The valve casing is formed in one side, below the top thereof, with a rectangular port 155 approximately centrally thereof and at the other side thereof with a pairof rectangular ports 156, 157 of greater length than the port'155. and the ports 156 and 157 are spaced fromthe port 155 and arranged on each side thereof. Near each end of the valve casing and at each side of the bottom thereof is arranged a rectangular port. The

I' ports at one end are indicated at 158 and 159 and at the other end at 160 and 161. vThe openings 150 and 154 are positioned in proximity to the ends of the valve casing and the openings 151, 152 and 153 are positioned intermediate the ends of the valve casing, The opening 152 is arranged approximately centrally thereof.

The port 126 formed in the piston rod 123 coacts with the port 158 and constitutes an exhaust port for space C of the piston cham- C of the piston chamber 120. The port 136 in the piston rod 132 coacts with the port 161 and provides an exhaust for the space B1 of the piston chamber 120. The two Vports 129, one in each piston rod, one in connection with the port 151 andthe other in connection with the'port- 153, provide pressure inlets for the'channel 146 and the two ports 130, one in each of the piston rods, one

' in connection lwith the port 1 56, and the Yother inconnection with the port i157 provide exhausts for the spaces B1 and B2 Voffthelpis-` ton chamber l120. The port 158'opensin the channel 147, port 159 opens in the channel- 148, port 156 opens in the channe-l1148", port 155 opens in the channel 147' and into the space C of the piston chamber 120` port '157 opens in the channel 148, vport 160 'opc'nsin the channel 147, and-port 161 opens inthe channel 148. Ports 150 to 154 inclusive open into the channel 146, and each of said ports has its edge provided with da packing tons toward the center, consequently the f valve 145 being thrown to the lett to close pressure port 152 into space C and opening exhaust ports 158 into' 126 and 160 into 135, the valve stem then remaining stationary; the piston rods 123 and 132 will move toward one another tending to close one of the ports 129 and to open the other port 129; hence port 129 in rod 123 has to be made longer than the other port 129, on the other hand' port 129 in rod 132 has to be made shorter than the other port 129 for exactly opposite reasons when pressure is applied in'spacexC as piston rod 132 is moving in a direction tending to uncover a port 153, the piston rod now having been drawn to the right and to cover ports 151, and 153. "Y

A pair of sectionalpressure supply passages are` employed and each of` which is referred to generally by the referen'cecharacter 81. Each pressure supply passage extends through a block 80, a block 83, a block87-and one of the shaftv sections4 92 or 93. They contour of each pressure supply passage Slis shown in Figure 2. The inner face of the shaft 59 near its inner end is formed with a set of spaced annular i grooves and the periphery of the shaft sec- .tion 92 is provided with. a set fof annular grooves. kThe grooves ,in the shaft section 59 and on` the shaft section 92 aresemi-circular in contour and the said sets of groovesregister to provide annular channels D1, D2 and D3. The shaft 60 and the shaft section 93v are sa esare clearly shown in Figure .2.` vOne i palr of exhaust passages is formed in the shaft section 92, shaft 59 and certain of the holders 78 of one set and the other pair of exhaust passages is formed in the shaft section 93, shaft and certain of the holders 78 of the other set, Each exhaust passage 164 is provided for exhausting from the space C of the piston chamber 120. One of the exhaust passages 165 is employed for exhausting from the space B2 o f the piston chamber 120 and the other exhaust passage 165 is employed for exhausting from the space B1 of the piston chamber 120. Both exhaust passages are set up in a direction parallel to the axis of the gear and slightly below the liquid line.

Each channel D2 is to connect sections of a pressure passage together. The channels D1 are to connect sections of each of the exhaust passages from space C together. One of the channels D3 is to connect sections of the exhaust passage from space B2 together and the other channel D3 is to connect sections of the exhaust passa e from the space B1 together. Between t e channels D1 and D2 at one side of the gear is interposed a acking to confine any liquid from the channe D2 to the inside of the gear. The same arrangement is had at the other side between channels D2, D3. When it is desired to fill the gear with liquid, the plugs 24 and 27 are removed after 'the gear has been placed in the position as shown in Figures 1, 1A and 1B. Plug 56 is then removed and one leg of a rubber tipped L-shaped piece of glass inserted through the opening 26. The rubber tipped end of the glass is extended into the opening 55 and the other leg of said L-shaped piece of glass is calibrated so that one .may knowhow much liquid to pour into the gear. The liquid is then poured into the gear through the open holes until the gear has received the required amount of liquid. It is evident if the level' of liquid should reach in further toward the center than the edges of the exhaust port the gear would not function properly, and thereore it should be carefully noted that too much liquid is not put into the ear.

lhe packing elements 85 an 86 are required to confine the liquid when the gear is idle. They are fixed inthedriving section, but clear the controller portion shghtly so that there will be a minimum amount of sliding friction between them an the controller section. When pressure is q erted against the packing, it will bear against the web portion thereof thus tending to rotate it outward from the axis of the gear and flattening against the grooves, securely binding it against the sides of the grooves thus preventing leakage.

Each pressure supply passage consists of a section H formed in a shaft section 92 or 93, a section H formed in a block 87, a section H formed in a block 80 and a section H formed in a block 83. The section H is disposed at an inclination, the section H curved, the section H curved, the inner portion of the section H curved. The sections H', H and the curved part of the section H extend upon the same arc and the remaining portionof the section H is disposed tan entially.

Each o the exhaust passages I164 or 165 consists of a section J formed in a shaft section 92 or 93, a section J formed in a shaft 59 or 60, a section J formed in a holder member 78 and the said section J has a right angular extension J opening at the outer side of a holder member. The exhaust passages 164 extend in an opposite direction with respect to the exhaust passages 165.

As to the actual operation of the gear, the driving member being constantly connected to the prime mover, as hereinbefore set forth, imparts a rotary movement to a body of liquid preferably of high conductivity, boilin point, good lubricating qualities, low coefhcient of friction on metal surfaces together with high. viscosity, and specific heat and sometimes high specific gravity which liquid acts as the elastic medium furnishing both potential and kinetic energy to convert high speed and low torque in the driver to low speed and high torque in the driven section.

Assuming that the gear is in its neutral position as shown and the driving section 1s travelling at the same angular speed as the driving member 50 and a forward drive is desired, the collar 117 is shifted to the right by the link and lever mechanism 118 and such action shifts the bar 116 in the same direction, which in turnwill move the valve stem 150 outwardly thus bringing the center of the port 152 in the valve casing 144, to the vertical central axis of the gear andi closing ports 151 and 153, at the same time moving exhaust port 159 for space B2 over exhaust port 128 and moving exhaust port 161 for space B1 over exhaust port 136. The liquid under pressure will flow down through sections H, H and H of the supply passage 81, and then around channel D2 until it meets section H of the supply passage, as section H cannot remain exactly coincident with the end of section H when the controller ortion is moving relative to the driven portion. Then the liquid under pressure fows down through section H, through ports 127 in the piston rods, through ports 150 and 154 into channel 146 and out through port 152, and mov pistons in opposite directions away from each other carrying their rods therewith forcing the liquid from space B2 through one of the ports 130 and port 156 and along channel 148 and out through ports 159, 128 into section J of the exhaust passage 165, around channel D3 and then out through sections J J and J of the exhaust passage 165 and into the space between the driving and the controlling sections. Simultaneously with this action the liquid from the space B1 is forced through the other port 130 and port 157 into channel 148 and ports 161 and 136 into the other exhaust passage where it is discharged. When the piston rods are moved in an opposite direction, the two clutching devices will become active so as to clutch together the controller and driven sections so that they will revolve as a unit, and each of the concavities 121 of the Huid controller will establish communication between and match the pair of ports 75 and 76.

Due to the enormous kinetic energy of the rapidly moving controller section, there may not at first be sufficient thrust exerted by the hydrostatic pressure to hold the clutching faces in alignment, and will bethrown out of alignment. The stroke of either piston backwards' towards the vertical central axis of the gear will be equal to twice the rise of the clutch faces and they will be forced into alignment again, however, and the cycle will be repeated until all the kinetic energy of the controller section is used up in pumping the liquid out of space C. Thus the clutch arrangement not only provides for positive alignment of parts of the gear, but also gra'dual engagement with a minimum amount of shock.

The fiuid under the impetus of the vanes enters the grooves or channels 74, ports 75, 76 and concavities 121. The Huid enters almost tangentially and describes an arc of 270 degrecs and emerging in a radial direction. The cross section of the passages or ports remain constant in area up to the 27() degree point from which station it deceases uniformly. rlhe total decrease in angle being aboiit 10 degrees. As stated the ends of the vanes 51 are bevelled or in other words they are tapered at an angle about degrees with their long radial Hank to direct the stream emerging from these passages in the direction of rotation of the driving member. The number of passages provided in the controller section will depend mainly upon the space limitations imposed and periphe 'al speed at which it is desired to operate the driving section; as their number is decreased with a proportional increase of cross sectional area of each, the stress on the segmental-shaped holders 78 decreases as the square of a greaterpower of the initial number of passages divided by the vchosen number of passages. Also if one can safely use high peripheral speeds, less cross sectional area of passages is required due to the increased arm of action, hydrostatic pressure and kinetic energy of theliquid.

Now suppose it is desired to travel from either. forward drive or neutral into reverse, then the link and lever mechanism 118 is actuated to shift the collar 117 to the left and which will shift the rod 116 also to the left and then Vvalve stem 150 Awill be moved inwardly, thus moving ports 151 and 153 to the left so that they open into the ports 129 of the piston rods, at the same time closing pressure supply port 152 which leads into space C and moving exhaust port 158 from space C over exhaust port 126 and also moving exhaust port 160 from space C over exhaust port 135. rl`he fluid under pressure will take the same course described in a previous paragraph in the groove 146, and from the latter it will pass out the ports 151 and 129. At the opposite end of the gear the liquid under pressure willflow down into the other piston rod to the other inlet port 127 in the casing 144, along groove 146 and out ports 153 and 129. The pistons will be caused to more towards each other and the liquid from space C will be forced out through the always openexhaust port 155 in the casing 144, along groove 148 in both directions and out through ports 158, 126, 160 and 125 to exhaust passages. The clutching mechanism will be moved in an opposite direction acting on the`controller section so that the latter will be held stationary to the housing. The liquid will flow through 180 degrees of the passages in the driving member striking the concave portions 122 of the fluid controller. As the liquid is now travelling in a direction exactly opposite to that in which it enters the driven shaft is reversed. The kinetic energy will first have to be taken up in pumping liquid as described in the preceding paragraph.

The mechanism heretofore described either binds the controller section at both ends to the driven section or to the frame or lets it iioat freely of either, thus giving the condition of a beam fixed at both ends to the eX- posed beam portions of the controller section allowing ne to use the minimum amount of material in their construction. Such a beam is six times as eflicient as a beam fixed at only one end.

This hydraulic gear gives an infinitevariation of speed in either forward or reverse direction of the driven shaft with the dri vingl section rotating at a constant high speed in one direction with the torque transmitted` to the driven section increasing as its speed decreases. It functions as stated in a small space and with few intricate parts. evident that the torque due to hydrostatic pressure of the liquid against the vanes will be constant at all times regardless of the direction or speed of rotation of the driven section, but the torque due to the kinetic 'energy of the rapidly moving liquid against the vanes will vary directly in proportion to the differences in the squares of the angular speeds of the driving vane and impeller. Hence the torque will increase as the difference in speed of the two increases, therefore it is thought themany advantages ofa hydraulic gear, for the purpose set forth, and in accordance with this invention, can

It isv be readily understood and althouglh the preferred embodiment of the invention is as illustrated and described, yet it is to be understood that changes in the details of construction can be had which will fall within the scope of the invention as claimed.

What I claim is 1. A hydraulic gear for transmitting power at a reduction comprising a revoluble driven section including means for rapidly rotating a body of liquid contained therein, a controlling section arranged concentrically with respect to and free of connection with said driving section and having means to provide for the flow of the liquid through it in a combined tangential and radial direction in relatively thin sheets, the longitudinal portions of said sheets being parallel to the longitudinal axis of the controlling section, said means of the controlling section providing for the revolving thereof, said controlling section arranged within said driving section, and a revoluble power transmitting driven section arranged concentrically to and within the controlling section and including means acted upon by the Huid driven from the driving section and conducted through the controlling section for operating said driven section and with the flow of the liquid with respect to said driven section being in the same direction as the flow with respect to the controlling section, means for coupling said controlling and driven sections together as'a unit to provide for the operation of the driven section in a forward direction, and further providing for the disconnection of the controlling and driven sections to allow the controlling section to revolve free of the driven section thus placing the drive in neutral.

2. A hydraulic gear for transmitting power at a reduction comprisinor a revoluble driven section including means Ior rapidly rotating a body of liquid contained therein, a controlling section arranged concentrically with respect to and free ofy connection with said driving section and having means to provide for the flow of the liquid through it in a combined tangential and radial direction in relatively thin sheets, the longitudinal portions of said sheets being parallel to the longitudinal axis of the controlling section, said means of the controlling section providing for the revolving thereof, said controlling section ar-y ranged within said driving section, a revoluble power transmitting driven section arran ed concentrically to and within the control ing section and includin means acted upon by the fluid driven from t e driving section and conducted through the controlling section for operatin said driven section and with the flow of the liquid with respect to said driven section being in the same direction as the ow with respect to the controlling section, means for coupling said controlling and driven sections together as a unit to provide for the operation of the driven section in a forward direction and further providing for the disconnection of the controlling and driven sections to allow the controlling section to revolve free of the driven section thus placing the drive in neutral, and 4means for holding the driven section stationary thus placing the gear in neutral.

3. In a hydraulic gear in accordance with claim l, said clutching and unclutching means in the form o'f a hydraulically actuated clutch consisting of a pair of pistons moving towards and away from one another by the pressure created by the fluid driven by the driving section through a spiral shaped passage in the controlling and driven sections, said spiral passage unwrapping from the aXis of rotation in a direction opposite to that of the direction of rotation of the driving sectin, a movable clutching element connected to said pistons, and said clutching element providing for connecting the controlling and driven sections together for a forward drive and for separating them for neutral.

4. In a hydraulic gear according to claim 2, said clutching and unclutching means in the form of a hydraulically actuated clutch includin a pair of pistons moving towards or away rom one another by the pressure created by the fluid driven by the driving section through a spiral shaped passage in the controlling and driven sections, said spiral passage unwrapping from the axis of rotation in a direction opposite to that of the direction of rotation of the driving section, a movable clutching element connected to said piston and providing for connecting the controlling and driven sections together for a forward drive or to separate them for neutral.

In testimony whereof, I aix my signature hereto.

SCOTT V. E. TAYLOR. 

